Internal combustion engine



Nov. l, 1938.

INTERNAL COMBUSTION ENGINE Filed Jan. 23, 1936 2 Sheets-Sheet l M.KADENACY 9 Nov. 1,

M. KADENACY INTERNAL COMBUSTION ENGINE Filed Jan. 2:5.- 1936sheets-sheet 2 Patented Nov. 1, 1938 UNITED STATES PATENT OFFICE.

application January 23, 1936, Serial No. 60,529

" In Great Britain February 11, 1935 38 Claims.

The applicant has found that in an internal combustion engine, thebehaviour of the gases is such as to lead to the conclusion that as aconsequence of the combustion of the charge, the burnt gases form a masshaving a high initial velocity and possessing properties similar tothose of a cylinder immediately the exhaust orifice commences to open.There is first a period of delay,

during which the burnt gases do not issue from the cylinder and afterthis delay has elapsed the burnt gases issue bodily from the cylinderwith an extremely high velocity as a mass which responds to the laws ofreflection and rebound and it leaves in the cylinder a profounddepression.

Subsequently, this outward motion of the burnt gases is reversed indirection and ii the gases are allowed to re-enter the cylinder theydestroy the depression leit therein. v

Accordingly the applicant has already proposed a method of chargingtwo-stroke cycle internal combustion engines which consists in openingthe admission orifice for the introduction of a fresh charge after theexhaust oriflce opens, but

only with the required delay to ensure that the burnt gases are thenmoving outwardly through the exhaust system as a consequence oi theirmass exit from the cylinder. I

The present invention relates to such engines,

40 but more generally to internal combustion engines or machineswhereinthe burnt gases, issue from the explosion chamber as a mass at aspeed much higher than that obtaining when adiabatic action only isinvolved and in such a short interval of time that they are dischargedwholly or substantially wholly from the working chamber.

In such engines or machines as a consequence of each exhaust operation,when the burnt gases are discharged through an exhaust duct, twopressureor impulse phases will be produced in the exhaust duct as a consequenceof the mass exit and return of the burnt gases, and one depression orsuction phase will be produced in the exhaust duct after the mass 0!burnt gases has left the cylinder and before it returns to the latter.

The intensity of the depression left in the working chamber by theexhaust gases when they leave the latter in mass form is very great.This depression exists in the cylinder and also the exhaust duct in aspace which may be several times greater than the volume of thecylinder.

The invention consists in a method of utilizing an internal combustionengine or machine wherein the burnt gases are evacuated from the workingchamber as a mass at a speed much higher than that obtaining whenadiabatic action only is involvedand in such a short interval of timethat they are discharged wholly or substantially wholly from the workingchai'nber for producing a flow of fluid external to the said engine,consisting in employing the periods of depression and impulse orpressure left and produced in the exhaust duct of the said engine by themass exit of the burnt gases from the cylinder into the exhaust systemin order to aspirate the said fluid and deliver the aspirated fluid to apoint of utilizatiom'disposal or storage.

The invention further consists in the combination of an internalcombustion engine or machine, wherein the burnt gases are evacuated fromthe working chamber of the engine or machine through a duct as a mass,at a speed much higher than that obtaining when adiabatic action only isinvolved and in such a short interval of time that they are dischargedwholly or substantially wholly from the working chamber with a pumphaving suction and delivery oriflces and a com munication with theinterior of the exhaust duct, at a point situated nearer the workingchamber than the point of return of the burnt gases within the exhaustduct, the arrangement being such that the depression left in the exhaustduct by the mass exit of the burnt gases from the work-'- ing chamberinitiates a suction stroke of the said pump and the shocks produced bythe mass exit of the burnt gases and/or the return 01 the said masstowards the cylinder initiates a delivery stroke of strokes of the saidpump.

In a practical embodiment of the invention the engine to which theinvention is applied is a twostroke cycle internal combustion engine ofthe kind wherein the void left in the cylinder by the mass exit of theburnt gases from the cylinder into the exhaust duct is utilized incharging the cylinder, by opening an inlet forthe introduction of thefresh charge after the exhaust oriflce opens, but only with the requireddelay to ensure that the burnt gases are then moving outwardly throughthe exhaust orifice or duct as a consequenceoi their mass exit from thecylinder.

The action which creates the suction eflect occurring in enginesaccording to the present invention originates in the working chamber inwhich the combustion has been effected and is propagated from thischamber into the exhaust duct and into the pump, in that this suctioneffect is caused by the exit of the burnt gases from the working chamberat a speed greatly in excess of that obtaining when adiabatic actiononly is involved and in such a short interval of time that it isdischarged as a mass.

In carrying out the present invention the natural tendency of the burntgases to project themselves from the cylinder as a mass should befacilitated and not opposed, that is to say the area of the exhaustoriflce available for the discharge of the burnt gases should be aslarge as possible and the interval of time in which the area requiredfor this discharge of the burnt gases is made available should be asshort as possible, in order to obtain the most satisfactory results.

As stated above the effects utilized in carrying out the presentinvention originate in the working chamber and are not produced by anyaction exerted by the exhaust duct but in carrying out the invention theexhaust duct should be of such a form that it permits the utilization ofthe actions in question. The exhaust pipe between the working chamberand the pump provided upon the exhaust duct should be free from abruptrestrictions or enlargement of crosssection and the connection betweenthe pump and the exhaust duct should be situated at a point nearer theworking chamber than the point of return of the burnt gases in theexhaust duct.

Some embodiments of the invention will now be described, simply by wayof example, and with reference to the accompanying drawings, in which:

Figure 1 is a curve of pressures and depressions taken in the exhaustduct of an engine during the exhaust period.

Figures 2, 3 and 4 illustrate examples of exhaust duct arrangementswhereby the depression left in the exhaust duct may be utilized in orderto aspirate a fluid, and the pressure impulses Occurring therein mayalso be utilized to deliver this "Pirated fluid.

Figure 5 shows an embodiment, in which the invention is employed forsupplying a supplementary charge of air to a two-stroke engine.

In Figure 3 the delivery is chiefly obtained by' the direct impulseproduced by the explosion gases upon issuing from the cylinder.

In Figure 4 the delivery is chiefly elected by the return impulse of thedischarged exhaust gases, and in Figure 2 both the direct impulse andthe return impulse of the exhaust gases are utilized.

If a record is taken of the pressure variations in the exhaust pipe ofan internal combustion engine of the kind referred to during theexhaustperiodacurvesimilartothatshowninFigurelmaybeobtainedinwhichEOrepresents the opening of exhaust, theordinates represent pressures above and below atmospheric presure andthe abscissa crank angles in degrees.

It should be mentioned that in the figure the pressum above and belowatmospheric pressure are not shown in scale relationship.

suchacurvemaybeobtainedforexampleby utilizing a stroboscopic deviceformed by a ported tube mounted in or on theexhaust duct and rotatingwith the engine and a stationary but angularly adjustable ported sleeveon this tube having its port connected to a manometer, a pressure ordepression impulse being obtained each time the port in the tube andsleeve coincide and a record being taken when a steady reading is givenon the manometer, the crank angle at which each reading is taken beingdetermined by the angular adjustment of the sleeve.

The curve shows clearly the two phases of pressure or impulse P, P thatoccur during the outflow and return of the gases'andthe interveningphase of depression D. This curve is characteristic for all internalcombustion engines of the kind referred to'but the moments at which theoutflow and return of the gases occur will vary.

The moments during the operation of the en gine at which the aspirationof fluid and the delivery of such aspirated fluid may be produced inaccordance with the invention, will be seen from Figure}.

In the first place, a delivery phase may be produced by the direct shockor impulse of the issuing exhaust gases which occurs very shortly afterthe opening of exhaust, as shown by the part P of the curve.

A depression is then formed in the cylinder and a little later adepression D is formed in tute a second delivery phase.

The cycle may thus be considered to occur in the following manner:aspiration of fluid on account of the depression existing in the exhaustduct; then the delivery of the aspirated fluid by the return impulse ofthe discharged gases which follows this depression and after a rotationof the crank through about 280", a second delivery by the direct impulseof the burnt gases from the following explosion.

It should be noted that the intensity of the phenomena described aboveis inversely proportional to the distance from the cylinder.Consequently, the communication with the interior of the. exhaust ductshould be located close to the cylinder.

In prior British specifications, the applicant has described internalcombustion engines in i which it is proposed to utilize the vacuum orhigh depression left in the cylinderby the explosion gases when theyissue from the cylinder as a mass in order to introduce a fresh chargethrough the main admission ports.

In an engine of this kind, the fresh charge admitted to the cylindercannot fill the complete cavity left in the cylinder and in the ex-.haust duct by the issuing gases for practical reasons depending upon theposition, shape and surface of the admission orifices.

In fact, the applicant has found that if an orifice is provided in theexhaust duct close to the cylinder and is opened to a source of gaseousfluid external to the exhaust duct, the volume of gas- 'eous fluid drawndirectly into the exhaust duct although the volume of gaseous fluiddrawn into the exhaust duct may be equal to this charge.

Consequently by providing a chamber communicating with the interior ofthe exhaust duct 0! an internal combustion engine, and with a source offluid external to the exhaust duct, this fluid can be aspirated into thesaid chamber and if desired it can be delivered into a receiver, whereit may be stored undera suitable or chosen pressure and from which itmay be utilized for supplying the engine or for any required purpose,and if desired the depression left in the cylinder by the issuingexhaust gases may still be utilized in order to introduce a fresh chargethrough the main admission ports. Suitable distribution means must beprovided so that the aspirated air or other gaseous fiuid will followthe required direction during the suction and delivery periods, and sothat it cannot return from the paths it is required to follow.

These means may for example consist of nonreturn valves or of controlledvalves or of means such as those described in British SpecificationsNos. 35069/33 and 25165/34.

The communication with the interior of the exhaust duct must be suitablyarranged to permit a utilization of the depression and pressure phasesin accordance with the invention, the communication may be so arrangedthat use is made chiefly of the return impulse of the exhaust gases orof both these impulses one after the other, for the purpose ofdelivering and/or compressing the aspirated charge. a

Figures 2, 3 and 4 illustrate three examples of arrangements of thecommunication with the interior of the exhaust duct.

Figure 2 illustrates an arrangement of intake which makes use of meanssuch as those described in the applicant's prior British SpecificationN0. 35069/33. In this figure, which may be considered as a sectionthrough, the exhaust duct of an internal combustion engine, the duct lisenlarged in order to receive a cone shaped obturator 2, the point ofwhich will face the cylinder and the concave base of which will beturned towards the outlet end of the exhaust pipe, this obturator beingarranged in relation to the walls of the duct in such a manner as topermit the outflow of the burnt gases and to prevent a return wave ofthese gases from re-entering the cylinder.

The part of the duct receiving the obturator 2 is provided with orifices3, an annular chamber 4 provided or formed around. the duct l, andhaving an outlet 5 for connection to a source of fluid external to theduct I.

In this example, the intake orifices 3 for the aspirated fluid arearranged so that the direct impulse and the return impulse of theexhaust gases will be transmitted in such a way that the aspirated gasesmay be delivered by the highest intensity of each of these twocompression agents although it will be understood that the intensity ofthe direct impulse will always be higher than that of the returnimpulse.

Figure 3 illustrates a form of intake which ensures that the directimpulse will have the greatest action in delivering the aspiratedcharge.

In this figure, the exhaust G is surrounded by an annular chamber 1having an outlet 8 and the duct is interrupted by an annular space 9establishing a communication between the chamber 1 and the interior ofthe duct 6. The walls of the chamber 1 are flared in continuation of thewalls of the duct on the side ior connection to the cylinder so as toensure that the direct impulse communicating with of the exhaust gaseswill be transmitted into this chamber.

A practical form of intake which chiefly facilitates the utilization ofthe return impulse, and which has given satisfactory results in practiceis illustrated in Figure 4.

In this figure the exhaust duct is formed by two portions i0 and Hconnected together by a chamber l2. The portion III of the duct isextended into the said chamber by means of a tubularelement l3 openinginto the portion H. and situated in the interior of a tubular element Hwhich extends the portion ll of the duct and stops short of the innerwall of the said chamber l2. The annular space left between the elementsl3 and I4 establishes a communication between the interior of theexhaust duct and the chamber 2.

The portion ll of the duct is adiustably connected with the chamber I!in order to permit a regulation of the distance between the free end ofthe element l4 and the internal wall of the chamber situated towards thecylinder.

The diameter of the free end of the element I3 is slightly smaller thanthat of,.the duct II and the element M at this point is"slightly fiaredso as to provide a passage of increasing section between the elements l3and Hi from the free end of the element l3.

The length of, the element I3 may also be regulated by means of thescrew connection provided between this'element and the duct -l0. Theseadjustments enable the action of the device to be varied so as to varythe relation between the suction and the delivery of fluid and theintensity of these actions which will be exerted through the outlet [5of the chamber l2.

Figure 5 shows an engine arrangement in which the aspirated fluid isdrawn from the atmosphere and the pressure impulses in the exhaust ductare utilized in order to deliver this aspirated air to a supplementaryinlet port on the cylinder.

This figure shows an engine cylinder 16 in which moves a piston I'I. Airis admitted by intake 2|; which, by way of example, is shown similar tothat illustrated in Figure 4 communicating with a first chamber 22.

It isof advantage for. the chamber 22 to be of tubular form because theaspirated charge and the exhaust gases that will deliver this chargewill be in contact with each other and it will be of interest to preventthem from mixing.

The chamber 22 is provided at its end remote from the exhaust duct witha suction valve 3| or the like communicating with an external source offluid, which in theexample will be the air of the atmosphere, and adelivery valve 32 or the like. This delivery valve is followed bychambers, which may according to requirements be tubular or in the formor reservoirs or may be simply ducts for storing, leading or presentingthe aspirated and delivered gas to its point 01 utilization.

In the example, the valve 32 leads through a duct 33 to a reservoir 3!itself connected to a duct 35 which leads the aspirated and deliveredgas to a point of utilization.

The operation of this apparatus may be compared to a piston pump inwhich the function of the piston is taken by the exhaust gases while inmass form in the exhaust duct which exhaust the chamber 22 during whatmay be considered as a downward stroke of the piston and then deliverthe charge thus aspirated by means of what may be considered as twoupward strokes of the piston.

An apparatus such as that described above may be employed for example asa compressor and the compressed charge thus obtained may be utilized forsupplying a charge of. air or combustible gas to the engine cylinder.

In the example, the duct 35 is put into communication with asupplementary admission orifice 26 provided upon the cylinder and servesfor supplying an additional charge of air under pressure to the engine,the main charge being admitted by atmospheric pressure through theorifice Hi. This additional charge may, for example be introduced at theend of the main admission in order to serve as correcting air, asdescribed in the applicant's prior British Specification No. 24372/34,or it may serve for supplying a charge at any chosen moment through asuitable distribution means. In this case a great advantage is obtainedas compared with the use of a compressor which draws power from theengine, is more costly, and complicates the construction.

The orifice 36 is controlled by any suitable means, for example by avalve. 31, operated by push rod 28 and rocker arm 39 as indicateddiagrammatically in the figure, in order to open at the chosen momentduring the cycle of operations of the engine.

It the delivery valve 22 is omitted and the air is delivered directly tothe admission valve 31, the engine will work at a more or less fixedspeed because in this case the moment of opening 01' the valve 21 willhave to coincide with a moment at which a charge is delivered from thechamber 22. But in the case when the chamber 22 delivers into thereservoir 34 through a non-return valve or equivalent means, the enginewill draw its charge from the reservoir 34 at the required moment andits speed will become independent of the moments at which the suctionand delivery stages occur in the chamber 22.

By suitably proportioning the chambers 22, 23,

- 24 and 35, the charge delivered from the chamber 22 may be stored orsupplied to the point of u ilization at or above atmospheric pressure.

In the example described with reference to Figure 5, instead ofsupplying the main charge to the engine by atmospheric pressure, thismain charge may be introduced by any suitable means, for example by acompressor ll, connected to the inlet port II by a duct ll as indicatedin Figure 5.

It should be noted that as shown in Figure 5, a piston element such as alight, freely movable disc I! may be arranged in the chamber 22, withoutin any way aflecting the principle of. operation of the device.

The invention is applicable to engines or machines having any number ofstrokes per cycle, but as only two strokes are essential to complete thecycle, the invention will most advintageously be applied to two strokecycle engines in which the charge is introduced, at or above atmosphericpressure, into the combustion chamber by utilizing the phenomenadescribed.

The valves employed for the suction and for the delivery oi an aspiratedfluid in an arrangement according to the invention may be simple ormultiple. These valves may be arrangedso as to provide a passage 01large area and they may have any shape provided they respond to rapidsuctions and equally rapid deliveries.

As stated above, these valves may be replaced by deflectors such asthose described in the applicants prior British Specification No.35069/33, but in this case the delivered fluid cannot be stored undercompression.

In this last example, it may be imagined that the delivery pulsations offresh air or of the fresh charge are synchronized with the appropriatemoments for the introduction of these gases into the engine cylinder, sothat the inlet opening for these gases will coincide with the moment atwhich a high pressure exists in the ducts that deliver the gases, whichpressure is produced by one of the delivery agents described above, thatis to say, either by the direct impulse or the return impulse of theexhaust gases after their reflection from the atmosphere external to thecylinder.

I claim:

l. A method for producing a flow of fluid ex ternal to an internalcombustion engine, consisting in employing the periods of depression andimpulse or pressure left and produced in the exhaust duct of the saidengine by the mass exit of the burnt gases from the cylinder into theexhaust system, in order to aspirate the said fluid, compress thisaspirated fluid and if desired deliver the aspirated fluid to areservoir which may be the engine cylinder.

2. A method for producing a flow of fluid external to an internalcombustion machine where.

in the burnt gases are evacuated from the working chamber as a mass at aspeed much higher than that obtaining when adiabatic action only isinvolved and in such a short interval of time that they are dischargedwholly or substantially wholly from the working chamber, consisting inemploying the periods of depression and impulse or pressure left andproduced in the exhaust duct oi the said machine by the mass exit of theburnt gases from the working chamber into the exhaust system in order toaspirate the said fluid and deliver the aspirated fluid to a point ofutilization, disposal, or storage.

3. A method for producing a flow of fluid external to an internalcombustion engine wherein the burnt gases are evacuated from the workingchamber as a mass at a speed much higher than that obtaining whenadiabatic action only is involved and in such a short interval of timethat they are discharged wholly or substantially wholly from the workingchamber, consisting in employing the periods of depression and impulseor pressure left and produced in the exhaust duct 0! the said engine bythe mass exit of the burnt gases from the working chamber into theexhaust system in order to aspirate the said fluid and deliver theaspirated fluid to a point of utilization, disposal, or storage.

4. The combination with an internal combustion machine comprising aworking chamber and an. exhaust orifice, wherein the burnt gases areevacuated from the working chamber of the machine through a duct as amass, at a speed much higher than that obtaining when adiabatic actiononly is involved and in such a short interval of time that they aredischarged wholly or substantially wholly from the working chamber, witha pump having suction and delivery orifices,.and a communication withthe interior oi the exhaust duct, at a point situated near the workingchamber than the point 01' return of the burnt gases within the exhaustduct, the arrangement being such that the depression left in the exhaustduct are evacuated from the working chamber of theengine through a ductas a mass, at a speed much higher than that obtaining when adiabaticaction only is involved and in such a short interval of time that theyare discharged wholly or substan tially wholly from the working chamberand wherein the void left in the working chamber by the mass exit of theburnt gases from the said chamber into the exhaust duct is utilized incharging the said chamber, means to open said inlet orifice for theintroduction of the fresh charge after the exhaust orifice opens, butonly with the required delay to ensure that the burnt gases are thenmoving outwardly through the exhaust orifice or duct as a consequence oftheir mass exit from the working chamber, with a pump having suction anddelivery orifices and a communication with the interior of the exhaustduct, at a point situated nearer the working chamber than the point ofreturn of-the burnt gases within the exhaust duct, the arrangement beingsuch that the depression left in the exhaust duct by the mass .exit ofthe burnt gases from the working chamber initiates a suction stroke ofthe said pump and the shocks produced by the return of the said masstowards the cylinder and of the next mass exit of the burnt gasesinitiate delivery strokes of the said pump.

6. A combination as claimed in claim 4, including a source of gaseousfluid, a conduit connecting said source to the suction. orifice of thepump, means for utilizing and storing said fluid, and a conduitconnecting said means with the delivery orifice of the pump and whereinthe pump includes a chamber having at one end said communication withthe exhaust duct and at points remote from the exhaust duct said suctionorifice and said delivery orifice.

'7. A combination as claimed in claim 4, including a source of gaseousfluid, a conduit connecting said source to the suction orifice of thepump, means for utilizing and storing said fluid, and a conduitconnecting said means with the delivery orifice of the pump, and whereinthe pump includes a chamber of tubular form having at one end saidcommunication with the exhaust duct and at points remote from theexhaust duct, said suction orifice and said delivery orifice.

8; The combination'with an internal combustion machine a workingchamber, and an exhaustorifice, wherein the burnt gases are evacuatedfrom the working chamber'of the machine through a duct as a mass, at aspeed much higher than that obtaining when adiabatic action only isinvolved and in such a short interval of time that they are dischargedwholly or substantially wholly from the working chamber, with a pumphaving suction and delivery orifices and a communication with theinterior of the exhaust duct, at a point situated nearer theworking'chamber than the point of return of the burnt gases within theexhaust duct, and means arranged in the exhaust duct in such a wayrelative to the communication between the exhaust duct and the said pumpas to ensure that the depression left in the exhaust duct by the massexit of the burnt gases from the working chamber initiates a suctionstroke of the said pump and that both the direct impact and the returnimpact of the burnt gases will deliver the charge aspirated into thepump.

9. A combination as claimed in claim 8, wherein the said means areformed by deflecting and refiecting'surfaces so arranged in the exhaustduct as to permit the free outward passage of the mass of burnt gasesand to oppose the return of the said gases to the working chamber whileat the same time serving to direct the impacts caused .by the said massof burnt gases on both its outward and return motions into the pump.

10. A combination as claimed in claim 4, including non-return valves forcontrolling the suction and delivery orifices and opening in the desireddirection under the efiect of a suction or of a delivery action andclosing automatically.

11. A combination as claimed in claim 4, including deflectors forcontrolling the suction and delivery orifices and permitting the passageof a fiuid in one direction and opposing the return of the saidfiuid.

12. A combination asclaimed in claim 4, including distribution means forcontrolling the suction and delivery orifices so that said orifices openand close at predetermined moments.

13. A combination as claimed in claim 4, wherein the suction orificecommunicates with the atmosphere.

14. A combination as claimed in claim 4, including a reservoir anda'conduit connecting the delivery orifice of the pump with the saidreservoir whereby fluid delivered by the pump may be stored or conveyed.or presented to a point of utilization.

' 15. A combination as claimed in claim 4, in-

cluding .a reservoir and a conduit connecting the delivery orifice ofthe pump with the said reservoir whereby fiuid delivered by the pump maybe stored under pressure in said chamber.

16. A combinationas claimed in claim 4, including a reservoir, a conduitconnecting the delivery orifice of the pump with said reservoir wherebyfluid delivered by the pump may be stored under pressure in saidreservoir, a supplementary admission orifice upon the working chamber, aconduit connecting said supplementary admission orifice with saidreservoir and means controlling said orifice to open said orifice at achosen moment during the cycle of operations of the machine and put theworking chamber into communication with the reservoir.

1'7. A combination as claimed in claim 5; including a source of gaseousfluid, a conduit connecting said source to the suction orifice of thepump, means for utilizing and storing said fluid and a conduitconnecting said means with the delivery orifice of the pump and whereinthe pump includes a chamber having at one end said communication withthe exhaust duct and voir whereby fluid delivered by the pump may bestored or conveyed or presented to a point oi. utilization.

21. A combination as claimed in claim 5, in-

cluding a reservoir and a conduit connecting the delivery orifice of thepump with the said reservoir whereby fluid delivered by the pump may bestored under pressure in said chamber.

22. A combination as claimed in claim 5, in-

10 cluding a reservoir, a conduit connecting the delivery orifice of thepump with said reservoir whereby fiuid delivered by the pump may bestored under pressure in said reservoir, a supplementary admissionorifice upon the working chamber, a conduit connecting saidsupplementary admission orifice with said reservoir and meanscontrolling said orifice to open said orifice at a chosenmoment duringthe cycle of operations of the machine and put the working chamber intocommunication with the reservoir.

23. A combination as claimed in claim 5, including a reservoir, aconduit connecting the delivery orifice oi the pump with said reservoirwhereby fiuid delivered by the pump may be stored under pressure in saidreservoir, a supplementary admission orifice upon the working chamber, aconduit connecting said supplementary admission orifice with saidreservoir and means controlling said orifice to open said orificetowards the commencement of the main atmospheric admission to put theworking chamber into communication with the reservoir and supply acorrecting charge of air to the working chamber.

24:. A combination as claimed in claim 5, in-

cluding a reservoir, a conduit connecting the delivery orifice of thepump with said reservoir whereby fiuid delivered by the pump may bestored under pressure in said reservoir, a supplementary admissionorifice upon the working chamber, a conduit connecting saidsupplementary admission orifice with said reservoir and meanscontrolling said orifice to open said orifice towards the end of themain atmospheric admission to put the working chamber into communicationwith the reservoir and supply a correcting charge of air to the workingchamber.

25. A combination as claimed in claim 5, including a reservoir, aconduit connecting the delivery orifice of the pump with said reservoirwhereby fiuid delivered by the pump may be stored under pressure in saidreservoir, a supplementary admission orifice upon the working chamber, aconduit connecting said supplementa y admission orifice with saidreservoir and means controlling said orifice to open said orifice tosupply a supercharge to the working chamber after the closure ofexhaust.

28. The combination with an internal combustion engine comprising aworking chamber, an

exhaust orifice, an inlet orifice, wherein the burnt gases are evacuatedfrom the working chamber or the engine through a duct as a mass, at aspeed much higher than that obtaining when adiabatic actlon only isinvolved and in such a short interval oi timethat they are dischargedwholly or.

substantially wholly from theworking chamber and wherein the void leftin the working chamber by the mas exit of the burnt gases from the saidchamber into the exhaust duct is utilized 7 in charging the saidchamber, by opening the inlet orifice for the introduction of the freshcharge after the exhaust orifice opens, but only with the required delayto ensure that the burnt gases are then moving outwardly throughtheexhaust nor-inceorduetasaceottheirmass exit from the working chamber,with a pump having suction and delivery orifices and a communicationwith the interior of the exhaust duct, at a point situated nearer theworking chamber than the point of return of the burnt gases within theexhaust duct, and means arranged in the exhaust duct in such a wayrelative to the communication between the exhaust duct and the said pumpas to ensure that the depression left in the exhaust duct by the massexit of the burnt gases from the working chamber initiates a suctionstroke of the said pump and that both the direct impact and the returnimpact of the burnt gases will deliver the charge aspirated into thepump.

2 7. A combination as claimed in claim 26, wherein the said means areformed by deflecting and reflecting surfaces so arranged'in the exhaustduct as to permit the free outward passage of the mass of burnt. gasesand to oppose the rewhile at the same time serving to direct the impactscaused by the said mass of burnt gases on both its outward and returnmotions into the pump.

28. A combination as claimed in claim 4, wherein the exhaust ductcomprises two longitudinally displaced portions, the portion nearer theworking chamber being of such length that the interruption in theexhaust duct provides an annular space at a point situated nearer theworking chamber than the point of return of the burnt gases within theexhaust duct, and including an annular-chamber enclosing the exhaustduct at the zone of said interruption, said annular cham-. ber havingwalls situated towards the working chamber fiared in continuation of thewalls of the duct and having a communication with said pump, wherebysaid annular space establishes a communication between the pump and theinterior of the exhaust duct via said chamber.

.29. The combination with an internal combustion machine comprising aworking chamber and exhaust orifice, wherein the burnt gases areevacuated from the working chamber of the machine through a duct as amass, at a speed much higher than that obtaining when adiabatic actiononly is involved and in such a short interval of time that they aredischarged wholly or substantially wholly from the working chamber, witha pump having suction and delivery orifices, the exhaust duct comprisingtwo longitudinally displaced portions, the portion nearer the workingchamber being of such length that the interruption in the exhaust ductprovides an annular space at a point situated nearer the working chamberthan the point of return of the burnt gases within the exhaust duct, andincluding an annular chamber enclosing the exhaust duct at the zone oisaid interruption, said annular chamber having walls situated towardsthe working chamber flared in continuation of the walls oi. the duct andhaving a communication with said pump, whereby said annular spaceestablishes a communication between the pump and the interior of theexhaust duct via said chamber and whereby the depression left in theexhaust duct by the mass exit of the burnt gases from the workingchamber initiates a suction stroke of the said pump and the shocksproduced by the return of the said mass towards thecylinder and of thenext mass exit of the burnt gases initiate delivery strokesoi the saidpump.

exhaust orifice, wherein the burnt gases are evacuated from the workingchamber'of the machine through a duct as a mass, at a speed much Ihigher than that obtaining when'adiabatic action only is involved and insuch a short interval of time that they are discharged wholly orsubstantially wholly from the working chamber, with a pump havingsuction and delivery orifices, the exhaust duct comprising twolongitudinally displaced portions, the portion nearer the workingchamber being of such length that an interruption in the exhaust ductoccurs at a point situated nearer the working chamber than the point ofreturn of the burnt gases within the exhaust duct, and including achamber. c'onnecting the two portions of the exhaust duct, an orifice insaid chamber, a conduit connecting said orifice to said pump, a firsttubular element situated in the interior of said chamber and extendingthe portion of the exhaust duct more distant from the working chambertowards theworking chamber and stopping short of an internal wall of thechamber connecting the exhaust duct portions, and a second tubularelement situated within the first tubular element and extending theportion of the exhaust duct nearer the working chamber towards the otherportion of the exhaust duct, the space between said tubular elementsestablishing a communication between the interior of the exhaust ductand the chamber connecting .the exhaust duct portions and thence to thepump whereby the depression left in the exhaust duct by the mass exit ofthe burnt gases from the working chamber initiates a suction stroke ofthesaid pump and the shocks produced by the return of the said masstowards the cylinder and of the next mass exit of the burnt gasesinitiate delivery strokes of the said pump.

31. The combination with an internal combustionmachine comprising aworking chamber and exhaust orifice, wherein the burnt gases areevacuated from the working chamber of the machine through a duct as amass, at a speed much higher than that obtaining when adiabatic actiononly is involved and in such a short interval of time that they aredischarged-wholly or substantially wholly from the working chamber, witha pump having suction and delivery orifices, the exhaust duct comprisingtwo longitudinally displaced portions, the portion nearer the workingchamber being of such length that an interruption in the exhaust ductoccurs at a point situated nearer the working chamber than the point ofreturn of the burnt gases within the exhaust duct, and including achamber connecting the two portions of the exhaust duct, an orificeinsaid chamber, a conduit connecting said orifice to said pump a firsttubular element situated in the interior of said chamber and extendingthe portion of the exhaust duct more distant from the working chambertowards the working chamber and stopping short of an internal wall ofthe chamber connecting the exhaust duct portions, and a second tubularelement situated within the first tubular element and extending theportion of the exhaust duct nearer the working chamber towards the otherportion of the exhaust duct, the space between said tubular elementsestablishing a communication between the interior of the exhaust ductand the chamber connecting the exhaust duct portions and thence to thepump whereby the depression left in the exhaust duct by the mass exit ofthe burnt gases from the working chamber initiates a suction stroke ofthe said pump and the shocks produced by the return of v tion. betweenthe suction and the delivery of ex-.

ternal fluid by the pump. r

32. The combination with an internal combustion machine comprising aworking chamber and exhaust orifice, wherein the burnt gases areevacuated from the working chamber of the machine through a duct as amass, at a speed much higher than that obtaining when adiabatic actiononly is involved and in such a short interval of time that they aredischarged wholly or substantially wholly from the working chamber, witha pump having suction and delivery orifices, the exhaust duct comprisingtwo longitudinally displaced portions, the portion nearer the workingchamber being of such length that an interruption in the exhaust ductoccurs at a point situated nearer the working chamber than the point ofreturn of the burnt gases within the exhaust duct, and including achamber connecting the two portions of the exhaust duct, an orifice insaid chamber, a conduit connecting said orifice to said pump, a firsttubular element situated in the interior of said chamber and extendingthe portion of the exhaust duct more distant firom the working chambertowards the working chamber and stopping short of an internal wall ofthe chamber connecting the exhaust duct portions, and a second tubularelement situated within the firsttubular element and extending theportion of the exhaust duct nearer the working chamber towards the otherportion of the exhaust duct, the space between said tubular elementsestablishing a communication between the interior of the exhaust ductand the chamber connecting the exhaust duct portions and thence to thepump whereby the depression left in the exhaust duct by the mass exit ofthe burnt gases from the working chamber initiates a suction stroke ofthe said pump and the shocks produced by the. return of the said masstowards the cylinder and of the next mass exit of the burnt gasesinitiate delivery strokes of the said pump, means being provided wherebythe length of one or the other of the two tubular elements can be variedin order to vary the action of the intake between the pump and theinterior of the exhaust duct and/or the relation between the suction andthe delivery of external fluid by the pump, the diameter of the free endof the second tubular element being slightly smaller than that of thefirst tubular element at this point, and the said first element beingflared at this point in order to permit the area of the annular inletaperture between the two tubular elements to be varied by a. relativelongitudinal movement of these elements.

33. The combination with an internal combustion machine comprising aworking chamber and exhaust orifice, wherein the burnt gases areevacuated from the working chamber of the machine through a duct as amass, at a speed much higher than that obtaining when adiabatic actionis involved and in such a short interval of :time that they aredischarged wholly or substantially wholly from the working, chamber,with a pump haying. suction and delivery orifices, the exhaust ductcomprising. two longitudinally displaced portions, the portion nearerthe working chamonly ber being of such length that an interruption inthe exhaust duct occurs at a point situated nearer the working chamberthan the point of return of the burnt gases within the exhaust duct, andincluding a chamber connecting the two portions of the exhaust duct, anorifice in said chamber, a conduit connecting said orifice to said pump,a first tubular element situated in the interior of said chamber andextending the portion of the exhaust duct more distant from the workingchamber towards the working chamber and stopping short of an internalwall of the chamber connecting the exhaust duct portions, and a secondtubular element situated within the first tubular element and extendingthe portion of the exhaust duct nearer the working chamber towards theother portion of the exhaust duct, the space between said tubularelements establishing a communication between the interior of theexhaust duct and the chamber connecting the exhaust duct portions andthence to the pump whereby the depression left in the exhaust duct bythe mass exit of the burnt gases from the working chamber initiates asuction stroke of the said pump and the shocks produced by the return ofthe said mass towards the cylinder and of the next mass exit of theburnt gases initiate delivery strokes of the said pump, means beingprovided whereby the length 0! one or the other of the two tubularelements can be varied in order to vary the action of the intake betweenthe pump and the interior oi the exhaust duct and/or the relationbetween the suction and the delivery of external fluid by the pump, thediameter 01 the free end oi the second tubular element being slightlysmaller than that of the first tubular ele m'ent at this point, and thesaid first element be-.

ing flared at this point so that the passage between the tubularelements increases in section from the free end of the second element inorder to permit the area of the annular inlet aperture between the twotubular elements to be varied by a relative longitudinal movement oithese elements.

34. The combination with an internal combustion engine comprising aworking chamber, an exhaust orifice and an inlet orifice, wherein theburnt gases are evacuated from the working chamber of the engine througha duct as a mass, at a speed much higher than that obtaining whenadiabatic action only is involved and in such a short interval oi timethat they are discharged wholly or substantially wholly from the workingchamber and wherein the void left in the working chamber by the massexit of the burnt gases from the said chamber into the exhaust duct isutilized in charging the said chamber, means to open said inlet orificefor the introduction of the fresh charge after the exhaust orificeopens, but only with the required delay to ensure that the burnt gasesare then moving outwardly through the exhaust orifice or duct as aconsequence of their mass exit from the working chamber, with a pumphaving suction and delivery orifices, the exhaust duct comprising twolongitudinally displaced portions, the portion nearer the workingchamber being of such length that the interruption in the exhaust ductprovides an annular space at a point situated nearer the working chamberthan the point 01' return of the burnt gases within the exhaust duct,and including an annularcha'mber enclosing the exhaust duct at the zoneof said interruption, said'annular chamber having walls situated towardsthe working chamber .fiared in continuation of the walls of the duct andhaving a communication with said pump, whereby said annular spaceestablishes a communication between the pump and the interior of theexhaust duct via said chamber and whereby the depression left in theexhaust duct by the mass exit of the burnt gases from the workingchamber initiates a suction stroke of the said pump and the shocksproduced by the return of the said mass towards the cylinder and of thenext mass exit of the burnt gases initiate delivery strokes of the saidpump.

35. The combination with an internal combustion comprising a workingchamber, an exhaust orifice and an inlet orifice, wherein the burntgases are evacuated from the working chamber of the engine through aduct as a mass, at a speed much higher than that obtaining whenadiabatic action only is involved and in such a short interval of timethat they are discharged wholly or substantially wholly from the workingchamber and wherein the void left in the working chamber by the massexit of the burnt gases from the said chamber into the exhaust duct isutilized in charging the said chamber, means to open said inlet orificefor the introduction of the fresh charge after the exhaust orificeopens, but only with the resuired delay to ensure that the burnt gasesare then moving outwardly through the exhaust orifice or duct as aconsequence of their mass exit from the working chamber, with a pumphaving suction and delivery orifices, the exhaust duct comprising twolongitudinally displaced portions, the portion nearer the workingchamber being oi such length that an interruption in the exhaust ductoccurs at a point situated nearer the working chamber than the point ofreturn of the burnt gases within the exhaust duct, and including achamber connecting the two portions of the exhaust duct, an orifice insaid chamber, a conduit connecting said orifice to said pump, a firsttubular element situated in the interior of said chamber and extendingthe por-, tion of the exhaust duct more distant from the working chambertowards the working chamber and stopping short of an internal wall ofthe chamber connecting the exhaust duct portions, and a second tubularelement situated within the first tubular element and extending theportion of the exhaust duct nearer the working chamber towards the otherportion 01' the exhaust duct, the space between said tubular elementsestablishing a communication between the interior of the exhaust ductand the chamber connecting the exhaust duct portions and thence to thepump whereby the depression left in the exhaust duct by the mass exit ofthe burnt gases from the working chamber initiates a suction stroke 01'the said pump and the shocks produced by ehe return oi the said masstowards the cylinder and 01' the next mass exit of the burnt gasesinitiate delivery strokes of the said pump.

36. The combination with an internal combustion engine comprising aworking chamber, an exhaust orifice and an inlet orifice, wherein theburnt gases are evacuated from the working chamber of theengine througha duct as a mass, at a speed much higher than that obtaining whenadiabatic action only is involved and in such a short interval of timethat they are discharged wholly or substantially wholly from the workingchamber and wherein the void left in the working chamber by the massexit of the burnt gases from the said chamber into the exhaust duct isutilized in charging the said chamber. means to open said inlet orificefor the introduction of the fresh charge after the exhaust orificeopens, but only with the required delay to ensure that the burnt gasesare then moving outwardly through the exhaust orifice or duct as aconsequence of their mass exit from the working chamber, with a pumphaving suction and delivery orifices, the exhaust duct comprising twolongitudinally displaced portions, the portion nearer the workingchamber being of such length that an interruption in the exhaust ductoccurs at a point situated nearer the working chamber than the point ofreturn of the burnt gases within the exhaust duct, and including achamber connecting the two portions of the exhaust duct, an orifice insaid chamber, a conduit connecting said orifice to said pump, a firsttubular element situated in the interior of said chamber and extendingthe portion of the exhaust duct more distant from the working chambertowards the working chamber and stopping short of an internal wall ofthe chamber connecting the exhaust duct portions, and a second tubularelement situated within the first tubular element and extending theportion of the exhaust duct nearer the working chamber towards the otherportion of the exhaust duct, the space between said tubular elementsestablishing a communication between the interior of the exhaust ductand the chamber connecting the exhaust duct portions and thence to thepump whereby the depression left in the exhaust duct by the mass exit ofthe burnt gases from the working chamber initiates a suction stroke ofthe said pump and the shocks produced by the return of the said masstowards the cylinder and of the next mass exit of the burnt gasesinitiate delivery strokes of the said pump, means being provided wherebythe length of one or the other of the two tubular elements can be variedin order to vary the action of the intake between the pump and theinterior of the exhaust duct and/or the relation between the suction andthe delivery of external fluid by the pump.

37. The combination with an internal combustion engine comprising aworking chamber, an exhaust orifice and an inlet orifice, wherein theburnt gases are evacuated from the working chamber of the engine througha duct as a mass, at a speed much higher than that obtaining whenadiabatic action only is involved and in such a short interval of timethat they are discharged wholly or substantially wholly from the workingchamber and whereby the void left in the working chamber by the massexit of the burnt gases from the said chamber into the ex haust duct isutilized in charging the said chamber, means to open said inlet orificefor the introduction of the fresh charge after the exhaust orificeopens. but only with the required delay to ensure that the burnt gasesare then moving outwardly through the exhaust orifice or duct as aconsequence of their mass exit from the working chamber. with a pumphaving suction and delivery orifices, the exhaust duct comprising twolongitudinally displaced portions, the portion nearer the workingchamber being of such length that an interruption in the exhaust ductoccurs at a point situated nearer the working chamber than the point ofreturn of the burnt gases within the exhaust duct, and including achamber connecting the two portions of the exhaust duct, an orifice insaid chamber, a conduit connecting said orifice to said pump, afirst'tubular element situated in the interior of said chamber andextending the portion of the exhaust duct more distant from the workingchamber towards the working chamber and stopping short of an internalwall of the chamber connecting the exhaust duct portions, and a secondtubular element situated within the first tubular element and extendingthe portion of the exhaust duct nearer the working chamber towards theother portion of the exhaust duct, the space between said tubularelements establishing a communication between the interior of theexhaust duct and the chamber connecting the exhaust duct portions andthence to the pump whereby the depression left in the exhaust duct bythe mass exit of the burnt gases from the working chamber initiates asuction stroke of the said pump and the shocks produced by the return ofthe said mass towards the cylinder and of the next mass exit of theburnt gases initiate delivery, strokes of the said pump, means beingprovided whereby the length of one or the other of the two tubularelements can be varied in order to vary the action of the intake betweenthe pump and the interior of the exhaust duct and/or the relationbetween the suction and the delivery of external fiuid by the pump, thediameter of the free end of the second tubular element being slightlysmaller than that of the first tubular element at this point, and thesaid first element being flared at this point in order to permit thearea of the annular inlet aperture between the two tubular elements tobe varied by a relative longitudinal movement of these elements'.

38. The combination with an internal combustion engine comprising aworking chamber, an exhaust orifice and an inlet orifice, wherein theburnt gases are evacuated from the working chamber of the engine througha duct as a mass, at a speed much higher than that obtaining whenadiabatic action only is involved and in such a short interval of timethat they are discharged wholly or substantially wholly from the workingchamber and wherein the void left in the working chamber by the massexit of the burnt gases from the said chamber into the exhaust duct isutilized in charging the said chamber, means to open said inlet orificefor the introduction of the fresh charge after the exhaust orificeopens, but only with the required delay to ensure that the burnt gasesare then moving outwardly through the exhaust orifice or duct as aconsequence of their mass exit from the working chamber, with a pumphaving suction and delivery orifices, the exhaust duct comprising twolongitudinally displaced portions, the portion nearer the workingchamber being of such length that an interruption in the exhaust ductoccurs at a point situated nearer the working chamber than the point ofreturn of the burnt gases within the exhaust duct, and including achamber connecting the two portions of the exhaust duct, an orifice insaid chamber, a conduit connecting said orifice to said pump, a firsttubular element situated in the interior of said chamber and extendingthe portion of the exhaust duct more distant from the working chambertowards the working chamber and stopping short of an internal wall 'ofthe chamber connecting the exhaust duct portions, and a second tubularelement situated withirT the first tubular element and extending theportion of the exhaust duct nearer the working chamber towards the otherportion of the exhaust duct, the space between said tubular elementsestablishing a communication between the interior of the exhaust ductand the chamber connecting the exhaust duct portions and thence to thepump whereby the depression left in the exhaust duct by the mass exit ofthe burnt gases from the working chamber initiates a suction stroke orthe said pump and the shocks produced by the return of the said masstowards the cylinder and of the next mass exit 01' the burnt gasesinitiate delivery strokes of the said pump, means being provided wherebythe length oi! one or the other 01 the two tubular elements can bevaried in order to vary the action oi! the intake between the pump andthe interior of the exhaust duct and/or the relation between the suctionand the delivery of a relative longitudinal movement oi. these ele- 10ments MICHEL KADENACY.

